Perforating machine



.F, 24, 1939. J. FOSSA PERFORATING MACHINE 4 Sheets-Sheet 1 Filed Feb. 15, 1957 Jan. 24, 1939, J. FossA PERFORATING MACHINE Filed Feb. 13) 1937 4 Sheets-Sheet 2 m M V Jan. 24, 1939. J FQSSA PERFORATING MACHINE Filed Feb. 13, 1937 4 Sheets-Sheet 3 Jan.'24, 191 39. I FOSSA 2,144,620

PERFORATING MACHINE Filed Feb. 13, 1937 4 Sheets-Sheet 4 Patented Jan. 24, 1939 UNITED STATES PERFORATING MACHINE Joseph Fossa, Lynn, Mass,

assignor to United Shoe Machinery Corporation, Paterson, N. J., a corporaticn of New Jersey Application February 13, 1937, Serial No. 125,594

22 Claims.

This invention relates to perforating machines and is herein illustrated as embodied in a machine for producing ornamental perforations in shoe part blanks such as Vamps or tips.

Perforating machines of the type referred to as heretofore constructed commonly comprise a punch which is movable heightwise of a work support to perforate a blank positioned thereon and movable transversely of the support subsequent to each punching operation to advance the work along the support thus toform a row of perforations in the blank, usually along edge portions thereof. These machines are usually operated at speeds to produce from 400 to 500 reciprocations of the punch per minute. In constructions heretofore in use the parts are subjected to considerable wear partly because of their inertia at the speeds mentioned and partly because of the play between the various parts which further results in noisy operation.

In view of the foregoing, it is an object of the present invention to provide a perforating machine of improved construction which can be satisfactorily operated quietly at comparatively high speeds without excessive wear of the parts.

To this end, and as illustrated, the invention consists in the provision of a perforating machine in which there is a work support, a punch mounted for movement heightwise of the support, and a continuously rotating cam spaced from the punch, together with a manually-controlled member between the cam and the punch and movable heightwise thereof for causing the cam to force the punch toward the work support to produce perforations in work positioned upon the support.

Preferably, and as shown, the punch is mounted at the free end of a lever pivotally connected to the frame of the machine and is resiliently forced toward the cam, the member for causing operation of the punch being in the form of a wedge having faces for engaging corresponding faces of the lever so that the wedge can be moved to take up the space between the cam and punch thereby to initiate one or more punching operations. As illustrated, the punch lever is oscillated to cause the punch to advance the Work along the support by means of a continuously oscillating drive shaft connected to the lever by a link the efiective length of which can be varied to vary the length of feed movements of the punch.

The construction above set forth eliminates play between the punch and its operating mechanism thereby reducing wear and noise in operation with the result that the machine can be satisfactorily operated at speeds of 1500 cycles or more, per minute, but at the same time the punch can be quickly rendered inoperative to perforate the work Without placing excessive strain upon the operating parts.

The invention further provides novel mechanism including means for ensuring a single op eration of the punch, a presser foot for holding down the work during portions of the cycle of operations and at such times as the cam is ineffective to cause operation of the punch, and an adjustable gage for guiding edge portions of the work as it is advanced over the support.

These and other features of the invention are disclosed in the accompanying drawings and in the following detailed specification and are set forth in the claims.

In the drawings,

Fig. 1 is a front elevation of a perforating machine illustrating one embodiment of my invention;

Fig. 2 is a plan view of the machine;

Fig. 3 is a side elevation partly in section of the machine;

Fig, 4 is a front elevation of a portion of the punch operating mechanism, parts of the machine being shown in section;

Fig. 5 is a side elevation partly in section of the punch operating mechanism;

Fig. 6 is a plan View partly in section of portions of the punch operating mechanism;

'I is a detailed view partially in section of the punch lever and the punch operating lever;

Fig. 8 is a vertical cross section taken along the line VIII-VIII of Fig. 7;

Fig. 9 is a detail of the members shown in Fig. 7 with the punch operating lever in inoperative position;

Fig. 10 is a side view partly in section of the punch reciprocating and feeding mechanism;

Fig. 11 is a rear view of the mechanism shown in Fig. 10;

Fig. 12 is a plan view of the mechanism shown in Fig. 10; and

Fig. 13 is a detail view partly in section showing the mechanism for centering the punch.

As illustrated in Figs. 1 and 3 the machine comprises a frame it carrying a work table 12 adapted to support work to be operated upon, such as a quarter or other shoe part, which can be advanced across the table into operative position relatively to a punch M which is arranged to be depressed by a earn it which causes the punch to penetrate the work, the punch it being mounted in a punch carrier and feed lever l8 which is oscillated to cause the punch to feed the work across the table between successive punching operations there being a presser foot 26 to hold the Work down upon the table during the punching operation, and an edge gage 22 to guide the work during feeding operations.

The punch I4 (Figs. 4, and comprises punch tubes 24 which are carried by a punch plate 26 mounted in a dovetailed groove 28 at the lower end of a shank 36 and held in a position in the groove by a retaining plate 32 and sets crew 34. The shank 36 has a cavity 36 through which the waste material formed in the punching operations may pass. The shank 36 is slidably mounted in an opening 31 in a boss 38 at the forward end of the lever I8, heightwise movement of the shank relatively to the boss being prevented by a collar 46 at the upper end of the shank. The lever I8 is mounted upon a horizontal pivot 42 which is carried at the lower end of an oscillating forked link 44 mounted upon a pin 46 on the frame I6. The forward end of the feed lever I8 which carries the boss 38 extends between upright portions 46 (Fig. 13) of an extension 50 of the frame, these upright portions being effective to guide the boss in its oscillating movements. The forward end of the lever I8 and the plunger are normally held in raised position by a spring 52 (Figs. 1, 5 and 10) carried by a curved rod 54, the upper end of the spring being secured to the frame and the lower end of the spring being connected to a pin 56 mounted in the lever I8 and having a flattened portion 58 which is adapted to engage the lower end of the rod 52 to limit upward movement of the punch.

For causing reciprocations of the punch at the will of the operator there is provided a wedge member 60 adapted to form an operative connection between the cam I6 and the lever I8. This wedge member 60 is carried by a link 62 which is arranged to be reciprocated under manual control by mechanism hereinafter described. The member 60 carries a hardened steel wear plate 64 secured thereto by screws 66 and by dowels 61. The underside of the member 60 is provided with cam teeth 68 (Figs. '7, 8 and 9) engageable by similar teeth 16 mounted upon opposite sides of the boss 38. As best shown in Fig. 9, the teeth 68 have beveled faces I2 terminating in flat portions I3 and the teeth 10 have corresponding beveled faces 14 and fiat faces 15, the construction being such that when the link 62 is in one position the member 66 rests upon the faces but when the link is moved to the left, in Fig. 10, the teeth 68 ride up on the teeth ID to raise the member 60 which is held in raised position when the teeth 66 rest upon the flat faces 15. The lever is shown in its raised position in Figs. 5, '7 and 8 and in its lower position in Figs. 9 and 10. In the lower position the wear plate 64 is clear of the high part of the cam by about one-thirty-seconds of an inch with the result that as the cam is rotated this motion is not transmitted to the lever I8. However, when the link 62 is moved to the left and assumes its upper position the wear plate 64 is operated upon by the cam to cause a depression of the forward end of the lever I8 and consequently of the plunger to produce a punching operation. The cam I6 is driven by a continuously operated drive shaft I6 mounted in the frame and rotated by means of a pulley I8. The cam is lubricated by oil felt 86 carried by a bracket 82 on the frame.

The mechanism for oscillating the lever I8 in producing work feeding movements of the punch comprises a shaft 84 (Figs. 3, 5, 6 and 10), which is driven by an eccentric 86 on the drive shaft '16 and through an arm 88. Upon the end of the shaft 84 is an enlarged portion 90 which is connected to the lever I8 by means of a link 62 mounted upon the pivot 42 and carrying a pin 94 through which is connected an adjustable link 96 which extends through a slot 98 in a sleeve IDIJ secured to the portion 90. The link 96 has a cylindrical portion I62 slidably mounted in the sleeve and located between nuts I04 which are arranged to be moved axially of the sleeve by a screw bolt I66 which extends through a screw plug I68 in the upper end of the sleeve, the adjustment being made by means of a nut II 0. A spring I I2 (Fig. 10) extending between the upper end of the sleeve and the link 96 tends to force the link upwardly along a line between the center of the pin 94 and the center of the shaft 84. Variation in the position of the link 94 thus will result in a variation of the throw of the lever I8 in such manner as to vary the length of feed of the punch. When the center of the pin 94 is positioned to coincide with the axis of the shaft 84 the link 62 will oscillate about the axis of the shaft without imparting any movement to the link I8 with the result that there is no feed movement of the punch. The link 96 is provided with a pointer II4 arranged to move along a scale II6 on the sleeve I00 during the adjustment of the link for the purpose of indicating the length of the feed. It is to be noted that when the pin 94 is brought into alinement with the axis of the shaft 84 the latter does not transmit motion to the link 92 with the result that there are no work feeding movements of the punch. This adjustment is usually made when it is desired to produce perforations at widely spaced points in the work.

Mechanism is provided for oscillating the link 62 under manual control to render the cam effective in causing perforating operations of the punch. This mechanism comprises a pin II8 (Figs. 5 and 10) connecting the link 62 to an arm I of a lever I22 mounted upon the pivot 42 and having a second arm I24 carrying a pivot I26 upon which is mounted one end of a link I28 the other end of which is connected at I30 to a plate I32 mounted upon the stud 46. The plate is adapted to be rotated by a forked lever I 34 mounted upon a pin I36 carried by the enlarged portion 90 on the end of the shaft 84. The lever I34 has two arms I38 having at their ends hooks I46 and. I42 adapted to engage, respectively, studs I44 and I46 secured to the plate I32. The lever I34 is continuously oscillated up and down by the shaft 84 and when the lever is rotated in either direction one of the hooks will, during the next oscillation of the lever, be brought into engagement with one of the studs and upon downward movement of the lever the plate I32 will be ro tated to effect movement of the link 62 in a lateral direction. As shown in Fig. 5, the hook I40 has just engaged the stud I44 and has rotated the plate I32 in a counterclockwise direction with the result that the link 62 has moved to the left to raise the wedge member 60 so that the cam I6 will be operative during its next rotation to force the punch toward the anvil. In Fig. 10 the hook I42 has just engaged the stud I46 and rotated the plate I32 in a clockwise direction with the result that the link 62 has been moved to the right and the wedge member 66 has been lowered so that the cam will not engage the striking plate 64 with the result that the punch will not be reciprocated, in a heightwise direction, but will merely oscillate back and forth with the lever !8.

The lever 33% is operated by springs I48 and IEii mounted upon a rod 52 one end of which is pivotally secured at i5 3 to the lever I34. The springs engage a block 556 carried by an arm I 58 on a shaft 68 which extends toward the rear of the machine (Figs. 2 and 3) and carries at its rear end an arm H52 connected to a treadle rod ltd. The arm I53 is normally forced in a counterclockwise direction in Fig. 1 by a spring I66 (Fig. 3) which presses upon the under side of the arm 82. The springs MS and its upon rotation of the arm iiiii resiliently force the lever 3 3 to one of its two extreme positions in which one or another of the hooks will be thrown into position to engage one of the studs upon the plate E32.

It is to be noted that the various oscillating parts, particularly the lever it, the link 52, and the lever 13% are made light in construction to reduce as far as possible the inertia of the parts.

In order to reduce the play between parts thereby to reduce noise and the likelihood of breaking or producing excessive wear of the various operating parts means is provided. for preventing rapid rotation of the plate I32. To this end, there is provided a stop plate I68 (Figs. 10 and i2) pivoted at Iii] upon the frame and arranged to engage either of two ears I12 formed upon the plate I 32. The movement of the stop plate about its pivot is frictionally retarded by means of a spring I74 mounted upon a stud FIB extending through slot 578 in the stop plate, the spring operating to press the plate tightly against the surface of the frame with the result that when the plate I32 is moved angularly in either direction one of the ears will engage the stop plate i555 and its movement retarded to the extent that it is brought gradually into one of its extreme positions.

The plate I32 is held in each of its extreme positions by means of a spring I80 (Fig. 1) surrounding a rod I82 one end of which is pivoted to the plate at IBQ and the other end of which is carried by a stud i855 on the frame. It is to be noted that after the plate I32 has been swung through an angle of about 10 in either direction from the line between pivots t6 and IE5 the spring ii fi will serve resiliently to hold it in its extreme position.

Mechanism is provided for holding the plate i325 substantially in the position shown in, Fig. 5 in which the wedge member is in. operative position for a sufficient time for a single punching o oration to take place. This mechanism comprises a lever E88 (Figs. 1 and 10) mounted upon the stud E85 and having a hook I90 adapted to engage a stud it? upon the arm 558 when the latter has been rotated in a clockwise direction by momentary actuation of the treadle rod I64, the hook and the stud being held in engaging position by a spring 595. When in this position the lever 588 will hold the arm down with the result that the spring 5 53 will rotate the lever I34 in a counterclockwise direction and hold it in that position while it oscillated up and down to engage the stud Hid, thus initiating a punching operation. As the plate 5 32 is rotated, however, a tail portion its thereof engages an end Hit of the lever I88 ing it in a direction to release the hook I95 from the stud so that upon the next oscillation of the lever I35 the hook M2 can engage the stud I46 to rotate the plate I32 in a direction to render the wedge member 60 inoperative.

I have provided a presser foot 20 adapted to hold the work down upon the anvil during the time the punch is penetrating the work and mechanism for intermittently raising the presser foot at such times as the punch feeds the work, this mechanism being such that the presser foot is held in its downward position when the cam is ineffective to operate the punch. As shown in Figs. .1, 4, 6 and 13 the presser foot 20 is carried by a frame bracket 5%, the presser foot being mounted upon a vertical slide i538 held in position on the bracket by a guideway 253i; secured to the bracket by screws 2232. The presser foot is normally forced in a downward direction toward the work support by a spring 283 extending between a perch 2134 on the top of the slide and a perch 206 on the bracket. The slide has a laterally extending projection 298 from which extends upwardly and laterally a hook 2I0 adapted to engage a second hook 2i 2 carried by a link 2I4 secured to a pivot 2 i5 mounted ecoentrically of the axis of the cam It. This arrangement is such that as the cam rotates the link 2 I4 will raise the presser foot against the tension of the spring 203 during that part of the rotation of the cam when the high part thereof is out of engagement with the wear plate 64, or in other words, at such a time as the lever H3 is being moved rearwardly to cause feed movements of the punch.

Mechanism is provided to insure that the presser foot 26 is down to hold the Work against the anvil when the wedge I56 is inoperative to cause reciprocations of the punch heightwise of the anvil. To this end, there is provided means for disconnecting the hook 2 !2 from the hook 2| when the wedge member is in its inoperative position. This mechanism comprises an arm 2I8 secured to the plate I 32 having pivotally connected thereto at 22% a rod 222 which extends downwardly and through a spring perch 224 fastened to the link 2H3. Surrounding the rod is a spring 225 which extends between a collar 228 and the spring perch 225, the end of the rod being provided with nuts 229 adapted to engage the spring perch 22d when the rod moves to the left in Fig. i which occurs when the plate I32 is moved in a clockwise direction, resulting in swinging the link 25% about its pivot ZIB so that the hook 252 is disconnected from the hook 2H] at such time as the wedge member 60 is inoperative. This results in the spring 2E3 forcing the presser foot 2t toward the work support. When the plate i3? is moved in the opposite direction the collar 22% forces the spring yieldingly against the spring perch 22 to force the hook 2I2 into position to engage the hook m.

In order to raise the p-resser foot 28 when, for example, it is desired to present the work into operative position beneath the punch or to remove the work from the machine, I have provided a manually-controlled device comprising a lever 238 (Fig. l), pivoted upon one of the frame portions 48 at 232, the upper portion of the lever being adapted to engage the under side of the projection 2538 to raise the presser foot 23. The lever 23h is operated by means of a rod 234 an end of which is secured to a lever 236 pivotally mounted at 233 (Figs. 2 and 3) upon the upper portion of the machine frame and operated by a treadle rod 248.

When perforations are to be formed along a curved edge portion of the work the work must be shifted angularly with the result that the punch is turned in its mounting during feed movements of the punch carrier. In order to return the punch to its normal position after such feed movement I have provided a punch centering device. This device comprises a plate 242 (Figs. 10 and 13) secured to the frame portions 48 by screws 244. The plate carries a plunger 246 pcsitioned in an opening 248 and forced by a spring 250 into engagement with the shank 30 of the punch. The plunger is pointed and adapted to enter a V-shaped groove 252 in the punch. When the punch is turned angularly relatively to the bracket which occurs when operating upon curved edge portions of the work when the lever I8 is moved forwardly the plunger, acting in the groove, tends to cause the punch to return to its original position. It is to be noted that angular movement of the punch is limited by pins 254 (Fig. 3) secured to the lever I8 upon opposite sides of the punch receiving opening and adapted to engage beveled surfaces 256 upon the lower portion of the shank 30.

The gage 22 is adapted to contact with edge portions of me work in order to guide the latter as it is fed past the face of the anvil in such manner that the perforations produced by the punch will be equally spaced from th edge of the work. The marginal portions of the work are held down adjacent to the edge gage by a hold'down member 251 (Fig. 4) secured to the shank portion of the gage by a screw 258. The holddown member is in the form of a leaf spring adapted to press upon the upper surface of the work, the amount of pressure exerted thereby .being adjustable by means of a set screw 259.

The gage 22 is secured in position relatively to the punch in the following manner. As shown in Figs. 4- and 6, the plate 242 has an extension which has therein a vertical solt 26I in which is positioned a projection 262 extending from the shank of the gage, said projection having a head 264 for retaining the shank in position in a lateral direction. The gage is normally forced downwardly and inwardly toward the direction of punch feeding movement by means of a spring 205 extending from a pin 268 carried by the shank of the gage to a pin 270 secured to the bracket. The work engaging portion of the gage can be adjusted inwardly or outwardly of the line of punch feeding movement by means of a screw 212, the end of which is adapted to engage the wall of one of the upright frame portions 48 thereby to limit inward movement of the gage.

In order to provide for movement of the gage into inoperative position when it is desired to operate upon central portions of the work there is provided a cam plate 214 pivoted at 215 in the plate 242 and having notches 216 and 278 adapted selectively to engage the projection 262 of the gage. As shown in Fig. 4, the projection is positioned in notch 216 of the cam in which position the gage is operatively located relatively to the punch. Upon rotation of the cam by a handle 280 the gage is raised upwardly and outwardly out of its operative position. During this movement the gage is moved outwardly by means of a guide member 282 which engages an edge portion 284 of the plate 242 which acts as a cam to force the gage outwardly.

I have provided an anvil to serve as a backing member to receive the blow of the punch after it has penetrated the work. This member preferably comprises a brass plate 292 (Fig. 4) which is supported at the upper end of a post 294 and clamped in position thereon by clamping members 296 and 298, the clamping member 298 being secured to the post by a screw 300. The clamping member 296 is arranged to be tightened against the plate to lock it in position in engagement with the member 298 by means of an adjusting screw 302 (Figs. 1 and 3), there being a spring 304 positioned between the post 294 in the clamping member 286 to force the latter outwardly when the screw is loosened.

The table I2 is divided into two sections 306 and 308 which surround the anvil 292 and are clamped together along a line 3I0 to form a smooth work supporting surface. The rear section 308 is provided with depending ears 3I I which are secured to the post 294 by screws 3I2. The forward section 306 of the table is provided with ears 3I4 which are pivotally mounted upon screw bolts 3I6 so that the section can be rotated forwardly about the axis of the bolts when it becomes necessary to replace or adjust the anvil 292. The forward section 306 is secured in position in contact with the rear section 308 by means of a leaf spring 3I8 adapted to engage a pin 328 carried by the rear section 308.

Vertical adjustment of the anvil relatively to the punch is obtainable by means of a wedge 322 adapted to engage a beveled face 324 at the lower of the post 294. The heightwise position of the post adjusted by a screw 326 engaging a portion 328 of the frame and having a collar 330 which enters a slot 332 in the wedge by which the latter can be moved in or out in order to accomplish adjustment of the post.

In the operation of the machine the treadle rod 240 is depressed to raise the presser foot 20 so that a blank can be located in operative position relatively to the punch I4 upon the table I2 after which the treadle rod is released to permit the presser foot to hold the blank upon the table. The treadle rod I64 is then depressed with the result that the arm I58 is moved in a clockwise direction (Fig. l) to force the lever I34 in a counterclockwise direction. Upon oscillation of the lever heightwise by the oscillation of the shaft 84, the hook I40 (Fig. 5) of the lever will engage the stud I44 of the plate I32 and effect counterclockwise rotation of the same causing link I 28 to rotate the lever I22 in a direction to move the link 62 to the left which effects movement of the teeth 68 upon the teeth until the wedge member 60 occupies its upper position (Fig. '7) with the wear plate 64 in engagement with the c0ntinuously rotating cam I6 which causes depression of the punch I4 to perforate the work. The lever 44 is then oscillated to move the punch lever I8 in a direction to cause the punch to advance the work along the table and then to return it to its original position. During this time the cam I6 through the link 2I4 raises the presser foot clear of the work but permits its return at the end of the return movement of the punch. This cycle of operations continues as long as the treadle is depressed but when it is released the hook 42 is pulled to the right and engages the stud I46 to move the plate I32 in a clockwise direction which causes the link 62 to move to the right with the result that the wedge is moved out of contact with the cam and the latter no longer causes operations of the punch which continues to oscillate back and forth with the lever I8 but is held spaced from the cam by the rod 54 which engages the pin 55. As the plate I32 rotates the lever 2| 8 (Fig. l) rotates with it causing the rod 222 to release the hook 2 I2 from the hook 2 I 0, thus permitting the presser foot to be depressed by the spring 203.

When a single perforation is to be produced a quick depression and release of the treadle rod moves the arm 158 in a clockwise direction (Fig. 1), until the hook I96 engages the stud I92 which retains the arms when the rod is released in position to force the lever !32 into position in which the hook 14% will engage the stud M4 causing movement of the wedge to depress the punch. During rotation of the plate E32 the tail portion I95 thereof rotates the lever 488 to release the arm I58 so that upon subsequent oscillation of the lever 134 the latter will operate to depress the wedge rendering the cam inoperative to move the punch.

Having described my invention, what I claim as new and desire to secure by Letters Patent of the United States is:

l. A perforating machine comprising a work support, a punch mounted for movement heightwise of the support, a rotary cam, manually controlled means normally forming an operative connection between the punch and cam for causing the punch to penetrate work positioned upon the support and operable selectively to disconnect the punch from the cam, and means for oscillating the punch transversely of the support to advance the work along the support.

2. A perforating machine comprising a work support, a punch mounted for movement heightwise of the support, a rotary cam spaced from the punch, and a wedge positioned between the cam and the punch and movable in a heightwise direction to cause the punch to penetrate work positioned upon the support.

3. A perforating machine comprising a frame, a work support carried by the frame, a punch pivotally mounted upon the frame for oscillation relatively to the support, a rotary cam, means normally operative to force the punch toward the cam, and a manually controlled member normally forming an operative connection between the punch and cam for causing movement of the punch toward the support and operable selectively to render the punch inoperative.

4. A perforating machine comprising a frame, a work support carried by the frame, a punch pivotally mounted upon the frame for oscillations heightwise and transversely of the support, a rotary cam, means normally operative to force the punch toward the cam, a stop for limiting movement of the punch toward the cam, and a wedge insertable between the punch and cam for forcing the punch toward the support to penetrate work positioned thereon.

5. A perforating machine comprising a frame, a work support carried by the frame, a punch carrier pivotally mounted upon the frame for movement transversely of the support, a punch mounted in the carrier, a rotary cam spaced from the punch carrier, and a wedge pivotally mounted upon the frame between the cam and punch carrier and movable to close the space between the cam and the punch for causing movement of the punch toward work positioned upon the Work support.

6. A perforating machine comprising a frame, a work support carried by the frame, a punch carrier pivotally mounted upon the frame and having a free end portion extending over the support, a rotary cam spaced from the free end of the punch carrier, a punch mounted in the carrier, a wedge member mounted upon the punch carrier, and manually controlled means for moving the wedge into position in engagement with the cam for causing downward movement of the punch toward the support.

'7. A perforating machine comprising a frame, a support carried by the frame, a punch carrier pivotally mounted upon the frame and having a free end portion which extends in a transverse direction over the support, a punch mounted in said free end portion, a rotary cam for causing movement of the punch toward the support, and means for oscillating the punch carrier transversely of the support to feed work positioned thereon.

8. A perforating machine comprising a frame, a work support carried by the frame, a punch carrier pivotally mounted upon the frame, a

punch positioned in the carrier, a rotary cam located adjacent to the punch carrier, a member between the punch carrier and the cam causing movements of the punch toward the support, means for controlling the operation of the member comprising a link pivotally mounted upon the frame, and manually controlled means for moving the link into either of its positions, thereby to move the member respectively into operative or inoperative relation to the cam.

9. A perforating machine comprising a frame, a work support carried by the frame, a punch lever pivotally mounted upon the frame, a punch carried at an end of the lever, a rotary cam, a wedge member movable into position between the cam and the lever for causing movement of the punch toward the support, means for oscillating the lever to cause the punch to advance work across the face of the support, means for moving the wedge into or out of operative position relatively to the cam comprising a lever pivotally mounted upon the frame and operatively connected to the wedge, a plate pivotally mounted upon the frame, a link connecting the plate and the lever, and a latch carried by the punch lever and oscillating therewith adapted to engage either of two projections carried by the plate and operable selectively to rotate the plate in either direction thereby to cause movement of the wedge.

10. A perforating machine comprising a frame, a work support carried by the frame, a lever pivotally mounted upon the frame, a punch carried by the lever, a rotary cam, means normally operative to force the punch toward the cam, means on the frame normally operable to space the punch from the cam, and means positioned between the punch and cam and selectively operable to take up the space between the punch and cam to cause movement of the punch toward the support.

11. A perforating machine comprising a frame, a work support carried by the frame, a lever pivotally mounted upon the frame and having a free end portion extending adjacent to the support, a punch mounted in the free end portion, a continu ously rotating cam for causing movement of the punch toward the support, manually operable means for selectively rendering the cam either operative or inoperative to move the punch, a presser foot slidably mounted upon the lever adjacent to the punch, means normally operative to force the presser foot toward the support, means operable intermittently to raise the presser foot, and means for rendering the last-mentioned means inoperable when the cam is rendered inoperative to move the punch.

12. A perforating machine comprising a frame, a work support carried by the frame, a punch carrier pivotally mounted upon the frame, a punch mounted upon a carrier, a rotary cam spaced from the punch carrier, a wedge movable into position between the punch carrier and cam for causing the cam to move the punch toward the support, a presser foot slidably mounted upon the punch carrier, means normally operative to force the presser foot toward the support, a member operatively connected to the cam for intermittently raising the presser foot, and means operable when the wedge is inoperative to cause movement of the punch for rendering the cam inoperative to raise the presser foot.

13. A perforating machine comprising a frame, a post carried by the frame, a table associated with the post and comprising two sections, one of which is fixedly secured to the post and the other of which is pivotally mounted thereon, and means for locking the movable section in fixed position.

14, A perforating machine comprising a frame, an anvil carried by the frame, a punch carrier pivotally mounted upon the frame, a. punch mounted upon the carrier, a plate carried by the punch carrier and having a slot therein, a gage member having a portion which normally extends into position adjacent to the punch and having a shank portion positioned in the slot, and a cam pivotally mounted upon the plate for moving the shank portion along the slot to locate the gage in inoperative position relatively to the anvil and punch.

15. A perforating machine comprising a frame, a lever pivotally mounted upon the frame and having a free end, a punch mounted in the free end of the lever, an oscillating shaft, a link connected to the lever and to the shaft for reciprocating the lever, and an adjustable connection between an end of the link and the shaft for varying the position of the end of the link relatively to the axis of the shaft thereby to vary the length of the stroke of the lever.

16. A perforating machine comprising a frame, a link pivoted upon the frame, a pin carried by the link, a punch lever one end of which is connected to the pin, a punch carried by the other end of the lever, an oscillating shaft, a movable pivot carried by the shaft, and a link connecting the pin and movable pivot for oscillating the punch lever.

1'7. A perforating machine comprising a frame, a link pivoted upon the frame, a pin carried by the link, a punch lever one end of which is con-,

nected to the pin, a punch carried by the other end of the lever, an oscillating shaft, a pivot carried by the shaft, a link connecting the pin and pivot for causing reciprocation of the lever to effect feed of work by the punch, and means varying the position of the pivot relatively to the axis of the shaft to vary the length of the work feed movements of the punch.

18. A perforating machine comprising a frame, a work support, a punch mounted upon the frame for movement heightwise of the support, a rotary cam for causing movement of the punch toward the support, a spring normally operative to force the punch toward the cam, means for spacing the punch from the cam, and manually controlled means between the cam and punch for causing one or more operations of the punch upon work positioned upon the support.

19. A perforating machine comprising a work support, a punch mounted for reciprocation to-- ward and from the support, a continuously rotating cam, means normally operative to force the punch toward the cam, a stop operative to limit movement of the punch toward the cam to insure clearance between the cam and punch, a wedge located between the cam and punch, and manually controlled means for rendering the wedge operable to cause the cam to depress the punch thereby to perforate work positioned upon the support.

20. A perforating machine comprising a work support, a punch carrier mounted for movement heightwise of the support, a punch mounted in the carrier, a continuously rotating cam, projections upon the carrier having an inclined face, and means for operatively connecting the cam to the punch comprising a member located between the cam and punch having an inclined face for engaging the corresponding face upon the carrier and a flat face for engaging the cam.

21. A perforating machine comprising a work support, a punch carrier mounted for movement heightwise of the support, a punch mounted in the carrier, a continuously rotating cam, projections upon the carrier having inclined faces, and means for operatively connecting the cam to the punch comprising a member located between the cam and punch having inclined faces for engaging the corresponding faces upon the carrier and a flat face for engaging the cam, and manually controlled means for varying the position of the member in a heightwise direction to move the flat face from inoperative position to a position in which it engages the cam.

22. A perforating machine comprising a work support, a rotary cam spaced from the support, a punch positioned between the support and the cam mounted for movement heightwise thereof, a member between the punch and cam for causing the punch to penetrate work positioned upon the support, means for initiating a punching operation comprising a link connected to said member, a rotatable plate for actuating the link, a continuously oscillating lever selectively movable into engagement with the plate for moving the plate in a direction to render the member inoperative or in a direction to render the mem ber operable to cause a punching operation, a manually operable member for moving the lever into engagement with the plate, and means for forcing the lever angularly in a direction to engage the plate during a portion of its oscillation.

JOSEPH FOSSA. 

